Torsional vibration damper

ABSTRACT

A torsional vibration damper with at least two parts that are rotatable about an axis and can turn relative to each other against the opposition of at least one coil spring. Support shoes are provided between the spring and an outer wall of the damper structure and are arranged to slide along the outer wall with the spring as it undergoes compression and relaxation. The support shoes include roller bodies to reduce sliding friction between the support shoes and the outer wall.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The invention relates to a torsional vibration damper, especially formotor vehicles, with at least two parts that are rotatable about an axisof rotation and are rotationally movable relative to each other againstthe reaction of at least one energy storage device, such as for examplea coil spring, extending in a circumferential direction of the torsionalvibration damper, and the two parts have regions by means of which theenergy storage device can be compressed, at least one of the relativelyrotatable parts has a wall region that axially overlaps at leastradially outer regions of the energy storage device and extendslongitudinally of the energy storage device.

2. Description of the Related Art

Such torsional vibration dampers in the form of so-called twin-massflywheels are known, for example, from DE-OS 4 117 582, DE-OS 4 214 655,DE-OS 4 414 584, DE-OS 4 420 927 and DE-OS 19522718.

An object of the present invention is to optimize the dampingcharacteristics of the above-mentioned type of torsional vibrationdampers. By the inventive arrangement features of a torsional vibrationdamper, it should also be ensured that it can be produced and installedin a particularly simple manner. It should be especially also be ensuredthat also at higher rotational speeds of the torsional vibration damper,its energy storage device, especially in the form of coil springs, canoptimally perform its intended functions.

SUMMARY OF THE INVENTION

In accordance with the invention, that is achieved with a torsionalvibration damper of the type described at the outset, in that the atleast one energy storage device is supported radially outwardly by atleast one support element that is arranged between the energy storagedevice and the portion of the wall region that overlaps the energystorage device and by in compression of the energy storage device ismovable along the wall, whereby the support element has at least onesupport shoe that engages at least one portion of the energy storagedevice, between which and the wall region at least one roller body isprovided that is rollable along a surface carried by the support shoe.The at least one roller body can therefore roll on a roller surfacecarried by the support shoe, so that then the support element or theassociated support shoe cannot generate any sliding friction that couldoppose an extension and relaxation of the energy storage device. Duringsuch rolling movement, the roller body is also supported by a rollingsurface that is carried by that wall region that axially overlaps theenergy storage device. Thereby it is ensured that the at least oneroller body can carry out a rolling movement at least relative tosections of the disclosed wall region. The at least one roller body canroll directly along sections that are non-rotatable with respect to thewall. However, it can be especially advisable to provide an intermediateelement between the at least one roller body and the wall region, thaton one hand is movable along the wall region and on the other hand formsa rolling surface for that at lest one roller element. By one sucharrangement the supporting element is therefore formed by the at leastone roller body, the support shoe that is arranged radially inside theroller element, and the intermediate part that is arranged radiallyoutside of the roller element.

In a particularly advantageous way the intermediate element, the atleast one roller body and the support shoe are combined as onestructural unit that is mountable as such. Insofar as no intermediateelement is necessary for forming the support element, the at least oneroller body or the bearing and the associated support shoe can becombined into a single structural unit. In order to form one suchstructural unit, corresponding connections are provided between theso-formed structural elements that on the one hand ensure solidarity andon the other hand ensure the necessary movability between the individualstructural elements. For example, snap-on connections can be utilized,whereby, for example, to that end one structural element can haveprojections, such as, for example, noses, that engage with movement playin correspondingly dimensioned guide grooves of another structuralelement.

By the existence of an intermediate element, it can be advantageous ifthe intermediate element is movable within limits relative to thesupport shoe and by a movement between those two structural elements theat least one roller body rolls on a surface of the support shoe as wellas on a surface of the intermediate element. Through the limitedmovability it is at least ensured that between the two rotatable partsof the torsional vibration damper, against the operation of the at leastone energy storage device at least one certain rotation angle in theclockwise direction, and/or opposite to the clockwise direction is madepossible in which no friction is produced by the support element. Byexceeding the stated limited angular movement the intermediate elementcan slide along a surface that is carried by a wall region that axiallyoverlaps the at least one energy storage device. On the basis of thethus-provided friction contact, a friction damping effect that isconnected parallel to the action of the energy storage device can beproduced. In accordance with a further embodiment possibility of thepresent invention, at least one roller element can be arranged betweenthe intermediate element and the noted wall region that overlies the atleast one energy storage device.

In order to ensure acceptable tilt stability of the support elements,and therewith to achieve good guidance of the support elements, it canbe especially advantageous to provide several roller bodies arranged oneafter the other, as seen in the circumferential direction of thetorsional vibration damper. Those roller bodies can be formed, forexample, by balls and/or rollers and/or needle rollers. The utilizationof needle rollers is particularly advantageous because they save spacein the radial direction, and on the basis of their lengthwise extenthave a good load capacity because at least linear contact with theadjacent surfaces is provided. When utilizing several roller bodies theycan advantageously be positioned relative to each other by a cage. Acage also has the additional advantage that it can be drawn upon toproduce a loss-free connection between the roller bodies and the furthercomponents that form a support element.

For producing a support element, it can be especially advantageous if atleast one of its formed components, for example the support shoe and/orthe intermediate element, is made of plastic. Although the rolling pathcan be formed directly by the material of the support shoe and/or theintermediate element, it is especially suitable, particularly ifplastics are utilized, to provide at least one of those parts with ametallic insert that forms a rolling pathway. Such a metallic insert canbe connected with one of the components, namely the support shoe and/orthe intermediate element, through a form-lick, such as, for example, asnap connection. Nevertheless, it can also be advantageous when such aninsert is embedded in the material of the intermediate element and/orthe support shoe during their production, which is an advantage whenplastic is utilized, for then the corresponding components or elementscan be produced by injection molding. It can be especially advantageouswhen the torsional vibration damper has at least two energy storagedevices that extend over at least 90°, in the circumferential directionof the torsional vibration damper, and are radially supported at leastat the ends of adjacent regions of the energy storage devices by asupport element. By the use of very long energy storage devices, suchas, foe example, coil springs, it can also be suitable to also providesupport elements in regions of such an energy storage device that liebetween its ends.

When utilizing energy storage devices with a large length/coil diameterratio, they can be formed as a single piece, or else also by severalshorter springs arranged one behind another.

When utilizing several shorter springs to form a long energy storagedevice it can be advantageous to provide a support element formed inaccordance with the invention at least between two adjacent shortersprings.

It can be especially advantageous when coil springs are utilized thatthey are guided in a curved retainer that is formed from regions of atleast one of two relatively rotatable parts, whereby that retainerthrough which the engaged coil spring wall regions are bounded and theat least one support shoe directly radially supports at least onewinding of the coil spring. For that purpose, the corresponding supportshe can have at least one region that at least partially engages aradially outer section of a spring winding, through which the supportshoe can be fixed in the longitudinal direction of the related coilspring. A connection can also be provided between the support shoe andthe coil spring that serves as a holder for the support shoe relative tothe coil spring in a direction perpendicular to the longitudinal axis ofthe coil spring.

Through one such arrangement of the torsional vibration damper, it isensured that the at least one support shoe or the support element has orremains in a defined position relative to the coil spring, and inaddition is securely held on the coil spring. Therethrough, thepossibility is provided to join the coil spring and the shoe as apreassembled unit to provide for the installation of the damper. Therebythe corresponding coil springs and the thereon-provided support elementscan already be properly assembled with each other during springproduction.

In an advantageous way the holder of the support shoe or the supportelement on the coil spring can take place over the region of the supportshoe which surrounds a winding of the coil spring, so that it has aforce-locking or a form-locking connection with the wire or thecorresponding winding. In an advantageous way, that connection can beformed as a snap connection, so that the shoes can be clipped onto thecorresponding coil springs.

The arrangement of the holder or connection between a support shoe and acoil spring can be formed in a advantageous way so that the holderprovided between the support shoe and at least one spring winding makespossible at least a small pivotal angular movement of the at least onewinding relative to the support shoe. It will thereby be ensured thatwhen the corresponding coil spring is compressed, the windings work orcan be deformed without a need to be exerted on the support shoe, whichwould cause a rotation or a twisting of the support shoe.

The allowable pivotal movement or the possible twist angle suitably liesbetween 2 and 10 degrees. That twist angle can also be dimensioned to begreater or less, depending upon the pitch of the windings in the regionof the support shoe. For an optimal functioning of the torsionalvibration damper, or to ensure an acceptable guidance and holding of thesupport shoes in accordance with the invention, it can be especiallyadvantageous when the at least one winding for supporting the at leastone winding encompassing region of the at least one support shoe thatthe wire that forms that winding encompass it relative to its crosssection as well as over its longitudinal extent.

Thereby a middle section of that region—viewed in the longitudinaldirection of the spring—can have no play or only a small amount of playrelative to the spring wire and that the section extending laterally ofthat middle section of that region at an increasing distance from themiddle region has an increased play relative to that spring wire.

In an advantageous way, the support shoe can have at lease one extensionthat is formed umbrella-like and that extends in the longitudinaldirection of the spring, namely starting from the positioning or holdingof the corresponding support shoe to the spring ensured region. In anadvantageous way, the support shoe can have a corresponding extension onboth sides to ensure positioning of the same on the spring. It canthereby also be appropriate for the extensions—viewed in thelongitudinal direction of the spring—to have a cross section thatdiminishes with increasing distance from the region of the support shoeencompassed by the spring winding. In an advantageous way that crosssection can be formed wedge-like. By virtue of such an arrangement ofthe extensions it will be ensured that also by centrifugal force loadingof the corresponding coil spring the deformation of the same that isproduced, at least until a comparatively high rotational speed of thedrive motor, no frictional contact exists between the surrounded springwindings and those extensions.

The one holder of a support shoe on a spring winding ensured region canadvantageously be formed in one piece with the support shoe. Forexample, the support shoes can be produced from plastic, for example byinjection molding. It can nevertheless also be advantageous when the oneretainer of the support shoe on an ensuring region of the coil is atleast partially formed by a separate component that has a connectionwith the basis body of the support shoe. That connection can be formed,for example, as a clip or snap connection. Nevertheless, the holderensuring component can also be injected in the basic material of thesupport shoe which can be especially realized in a simple way byutilizing plastic. The connection or the holder region formed componentcan have at least a U-shaped cross section that forms two side legs thatare received between the corresponding spring windings. Theabove-described separate component can be produced of spring steel or ofa plastic material having suitable characteristics.

In an advantageous way, the support shoe—viewed in the circumferentialdirection of the spring windings—can have a cross section that has acurved or U-shaped course. It can thereby be appropriate when thesupport shoe is arranged in such a way that the spring windings of thecoil spring surround it over an angle of at least 90 degrees. It canalso be suitable for the support shoe to have an angular recess of atleast 180 degrees. In an advantageous way, the support shoe can also beformed in such a way that it bounds an inner surface that extends overmore than 180 degrees about at least one spring winding through which anoperative form locking connection is produced that is perpendicular tothe longitudinal axis of the coil spring. By such an arrangement of asupport shoe it therefore encompasses the coil spring in such a way thata form-locking connection is provided between the support shoe and thecoil spring.

The inventive arrangement can have particular application in connectionwith compression coil springs, which have a large length to windingouter diameter ratio. That can lie in the order of magnitude of from 5to 20. With springs of that type several support shoes or supportelements can be provided on them in an advantageous way. Thedistribution of those support elements over the length of a spring canparticularly take place in such a way that upon blockage of at leastsections of windings the support elements are not in contact with eachother. The support elements provided at the end sections of such aspring are staggered in an advantageous way so that single springwindings are freely deformable, without which friction produced througha support element opposes the deformation.

BRIEF DESCRIPTION OF THE DRAWINGS

Further advantages, construction features, and functionalcharacteristics of torsional vibration dampers formed in accordance withthe invention appear in the following description, in which by referencenumerals on the drawings different embodiments are described.

There is shown:

FIG. 1 a section through a damper unit by which the inventive solutionscan be established,

FIG. 2 the arrangement of a coil spring that can be utilized in a damperunit in accordance with FIG. 1,

FIGS. 3 to 5 a configuration possibility of a support element that canbe utilized in connection with an arrangement in accordance with FIGS. 1and 2,

FIGS. 6 and 7 a further configuration possibility of a support elementfor a coil spring,

FIG. 8 an additional embodiment of a support element,

FIGS. 9, 10 and 11, 12, 13 and 14 or 15, 16, 17 and 18 furtherarrangement and construction possibilities of different support elementsand

FIGS. 19 to 21 further advantageous details for the function of slideelements.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The torsional vibration damper 1 that is shown in section in FIGS. 1 and2 is formed as a divided flywheel that has a first or primary flywheelpart or inertial mass 2 attachable to a not shown output shaft of aninternal combustion engine, as well as a second or secondary flywheelpart or inertial mass 3. A friction clutch is attachable to the secondinertial mass 3 through an intermediate clutch disc, through which analso not shown input shaft of transmission is coupleable anduncoupleable. The inertial masses 2 and 3 are rotatable relative to eachother by way of a bearing 4 that, in the illustrated embodiment hasbores 5 arranged radially outwardly for the passage of securing screwsfor mounting the first inertial mass 2 on the output shaft of aninternal combustion engine. A damper unit 6, that includes energystorage device 7, of which at least one of which is formed ofcompression coil springs 8, 9, is operative between both inertial masses2 and 3. Compression coil spring 9 is at least partially received in thespace that is formed by the winding of spring 8, or, in other words,both compression coil springs 8 and 9 are viewed over their longitudinalextent as nested together. It can be appropriate if the spring 9—viewedin the circumferential direction of the torsional vibration damper—isshorter relative to the outer spring 8, for example, of the order offrom 10 to 60 angular degrees, preferably in the region of 10 to 40angular degrees. The length difference or the angular difference can,however, also be larger or smaller.

Both inertial masses 2 and 3 have contact regions 14, 15, and,respectively, 16 for the energy storage devices 7. In the illustratedembodiment, the contact regions 14, 15 are formed by stamped embossmentson plate portions 17, 18 that form part of the first inertial mass 2.The contact regions 16 that are provided axially between the contactregions 14, 15 are formed by at least one flange-like component 20 thatis connected to the secondary inertial mass 3, for example by rivets 19.The component 20 serves as a torque transmitting element between theenergy storage devices 7 and the inertial mass 3. The contact regions 16are formed by radial arms or extensions 16 that are provided at theouter periphery of the flange-like contact means 20. The component 17,produced by cold forming sheet material, serves to secure the firstinertial mass 2 or the entire divided flywheel 1 on the output shaft ofan internal combustion engine. Radially outwardly the component 17 isconnected with the component 18 that likewise is also made from sheetmetal. Both components 17 and 18 form an annular chamber 21 that hereforms a torus-like region 22. The annular chamber 21 or the torus-likeregion 22 can be at least partially filled with a viscous medium, suchas, for example, grease. Viewed in the circumferential direction betweenthe formations or contact regions 14, 15, the components 17, 18 formseats or bulges 23, 24 that border the torus-like region 22 and formseats for the energy storage devices 7. At least during rotation ofsystem 1, the springs 8 are supported by the radially outwardly boundedregions 17 a of the component 17 and/or 18 of the rim-like or torus-likeregion 22. The support of coil spring 8 takes place through theintermediary of support elements 25 that radially outwardly can be movedalong the regions 17 a in the circumferential direction of the torsionalvibration damper and radially inwardly support at least one winding 8 aof the spring 8. In the illustrated embodiment there is provided atleast one wear protector 26 that is formed by a hardened intermediateplate or plate insert, against which at least the support elements 25are radially supported. The wear protector 26 extends in thecircumferential direction in an advantageous way at least along theentire length or angular extent of the untensioned energy storagedevices 7. As a result of the centrifugal support of the energy storagedevices 7, insofar as there is provided a frictional engagement betweenthe support elements 25 and the regions 17 a that overlie the energystorage devices or the wear protector 26, a rotational-speed-dependentfrictional damping is produced by the length change or compression ofthe energy storage devices 7, or the coil springs 8, 9.

The radially extending component 17 radially inwardly carries anintermediate part or hub 27, that respectively receives or carries theinner race of ball bearing 4. The outer race of ball bearing 4 carriesthe inertial mass 3.

On the basis of the above, possible friction can develop between theindividual support elements 25 and the wear protector 26, especially athigh engine rotational speeds and small, or insufficient, slackening ofthe energy storage device 7, whereby the damping characteristics of thetorsional vibration damper can be reduced. Especially upon theoccurrence of changes (acceleration/deceleration) by the operation of amotor vehicle, disturbing noises can thereby result, namely because theenergy storer 7 then acts as a comparatively hard stop because thespring windings of the energy storer 7 remain in an at least partiallytensioned condition as a result of the above-mentioned friction andthereby produce a high spring rigidity.

In order to avoid that, or at least to ensure a substantially greaterrelaxation of the energy storer, or at least of the coil spring 8 alsoat higher engine rotational speeds, special support elements 25 comeinto operation, that are fixed at least to a radially outer section 50of a winding 8 a of the coil spring 8. Through the centrifugal forceexerted on the energy storage device 7 by the rotation of the torsionalvibration damper 1, the supporting elements 25 are pressed outwardly andsupported by the at least radially outer encircling wall regions 17 a ofthe energy storage device 7. In the illustrated embodiment, the supportelements 25 directly bear against the wall regions 17 a or the wearprotector 26.

The support elements that are shown in FIGS. 1 and 2 are shown in anenlarged scale in FIGS. 3 to 5. As can be gathered from FIGS. 3 to 5, asupport element 25 is composed of a support shoe 27 and a roller bodyarrangement 28, that is arranged radially between the support shoe 27and the wear protector 26. The roller body arrangement 28 is herecomposed of a plurality of needle rollers 29 (for example according toDIN 5402) arranged one after the other, as seen in the circumferentialdirection of the divided flywheel 1, that are positioned relative toeach other and held against loss by a cage 30. The roller bodyarrangement 28 therefore forms a linear guide for the support shoe 27.As can be gathered from FIG. 4, a connection by means of snap connectors31 is present between the cage 30 and the associated support shoe 27,which permits a circumferential displacement of roller body arrangement28 and the cage 30, however ensuring retention between the roller bodyarrangement 28 and the support shoe 27 in the radial direction of thetorsional vibration damper 1.

As can be gathered from FIG. 3, which shows the roller body arrangement28 in a middle position relative to the support shoe 27, the roller bodyarrangement 28 is received in a recess 32 of the support shoe 27, infact with rotational play 33, 34. Accordingly, the rolling bodies 29 canroll along the rolling surface 35 of the support shoe 27, so that bythat play no friction is produced by the support element 25 duringcompression and relaxation of an energy storage device 7.

In the exemplary embodiment, the rolling surface 35 is formed by ametallic insert 36 that is provided in the base of the recess ordepression 32 for the rolling element arrangement 28.

As can be seen in connection with FIGS. 3 and 5, a support shoe 27 hasboundary means that limits the movement of the roller body arrangement28 relative to the corresponding support shoe 27. In the illustratedexemplary embodiment, those boundary means are formed by end stops 37,38, that define the recess 32.

As can be gathered from FIG. 5, unconfined movement of the rollingbodies 29 is no longer possible by continued relative rotation betweenthe wear protector 26 and the support element 25. That means that byforcibly continuing a corresponding relative rotation the rolling bodyarrangement 28 is pushed along the wear protector against the end stop37 so that friction results between the roller bodies 29 and thecorresponding surface 26 a of the wear protector 26, that is controlledin parallel with the elasticity of the corresponding energy storagedevice 7.

It is advisable to dimension the illustrated rotational clearances 33,34 shown in FIG. 3 in such a way that they permit a relative rotation ofat least two angular degrees between the input and output part of thetorsional vibration damper 1, that is, here between the primary inertialmass 2 and the secondary inertial mass 3. However, preferably thatpossible rotational angle is designed to be as large as possible.Preferably, clearance is provided between the roller body arrangement 28of roller bodies 29 and the support shoe 27 that corresponds with arotation angle of at least 2° between the two inertial masses 2 and 3.

Through the inventive arrangement, a supporting element 25 it canthereby be ensured that, at least over the provided movement clearance33+34 between the roller body arrangement 28 and the support shoe 27,the supported windings of an energy storage device, or at least one coilspring, can freely operate. Thereby it is ensured also at highrotational speeds of the torsional vibration damper a least a partial,free compression and relaxation of the energy storage device or the atleast one coil spring. In the exemplary embodiment illustrated in FIG. 2all support elements 25 are provided with a roller body arrangement 28in accordance with the invention. However, it can be advisable toprovide such a support element 25 only in the adjacent regions of theenergy storage device 7 or coil spring 8 at the circumferential ends ofthe energy storage device 7 or coil spring 8, so that also at higherrotational speeds at least the end regions of the corresponding energystorage devices can be freely relaxed over a specified angle or over aspecified distance. Particularly in the middle region of an energystorage device 7 support elements 125 can be utilized, as can begathered from FIG. 8. The support element 125 illustrated in FIG. 8 doesnot have a roller body arrangement but only has a support shoe 127formed as a slide shoe that has a suitable frictional engagement withthe associated support surface 126 a. In an advantageous way such shoes125 can be combined with support elements 25 in accordance with theinvention. The circumferential arrangement or sequence of such supportelements 25, 125 can be made corresponding with the necessary or thedesired damping effect. For many applications it can however be suitableto provide at least one support element 25 in accordance with theinvention on at least one end region of a long energy storage device

FIGS. 6 and 7 illustrate a further possible configuration of a supportelement 225. Support element 225 differs relative to a support element25 in accordance with FIGS. 3 to 5 essentially in that it has anadditional intermediate element 240 that is arranged radially outwardlyof the roller body arrangement 228. The intermediate element 240 is, inturn, supported by a wall along which it is slidable. That wall can, inturn, be formed by a band-shaped wear protector 26 that was morespecifically described in relation to FIGS. 1 to 5, for example. Theintermediate element 240 forms a rolling surface 241 for the rollerbodies 229 of the roller body arrangement 228. In the illustratedexemplary embodiment, the rolling surface 241 is formed by a metallicinsert 242 that is embedded in the base material of the intermediateelement 240.

As can be gathered from FIGS. 6 and 7, the utilization of anintermediate element 240 enables doubling the possible movement path orthe possible rotation angle between the support shoe 227 that directlyradially supports at least one spring winding and the radially outersupport regions of the support element 228, such as, for example, asalready explained, by a wear protector 26. It can be gathered, forexample, from FIG. 6, that the rotation clearance 243, 244 of that shoethat is provided at both sides of a support shoe 227 relative to theintermediate element 240 is twice as large as the possible rotationclearance 233, 244 between the roller body arrangement 228 and thecorresponding support shoe 227.

As can be gathered from FIG. 7, the regions 238, 239 of a support shoe227 serve as stops that cooperate with opposed stops 245, 246 providedon the intermediate element 240 to limit the relative movement between asupport shoe 227 and the associated intermediate element 240.

In an advantageous way, the displacement resistance of an intermediateelement 240 as described in connection with FIG. 1 it can be reduced byan at least partial filling of the annular chamber 21 with a lubricant,for example, grease.

Furthermore, it can be especially advantageous when, in order to improvethe structure of a lubrication film, at least one of the surfaces thatare in frictional contact with each other has at least a smooth surfacestructure that favors the retention of a lubricant, such as grease,between the intermediate elements 240 and the supporting surfaces. Thelatter can be achieved, for example, by providing a certain unevennessor roughness on at least at one of the cooperating slide or supportsurfaces 26 a, 247. In an advantageous way, at least one of thecooperating slide or support surfaces 26 a, 247 can have a coating, suchas is the case, for example, in sliding bearings. Such slide surfacescan contain, for example, PTFE, graphite or copper.

In an advantageous way, the intermediate elements 240 can be composed ofplastic, whereby they can be produced in a simple way, namely byinjection molding.

The support elements, especially in the form of slide shoes, can also beproduced from a different material, for example those regions of asupport element that engage the energy storage devices or the coilsprings can be made of polyethylene-etherketone (PEEK) orfiber-reinforced polyamide (PA) 4.6. The support elements or slide shoescan also have an insert, for example metal reinforcement. One suchmetallic insert can be produced as a sheet metal formed part or as aninjection molded part. As already mentioned, those regions that formslide surfaces of a support element can be composed of a low wearmaterial. For example, non-reinforced PA 4.6TF30 can be utilized.Several plastics can also contain a slide-layer-forming material, forexample, lead, tin and/or copper. On such composition can contain, forexample, 9 to 11% lead, 9 to 11% tin, wherein the remaining portion canbe composed of copper. If necessary, the slide layer can additionally beprovided with an inlet layer that has a thickness in the order ofmagnitude of, for example, from 0.01 mm to 0.03 mm. One such inlet layercan be composed of PTFE and/or lead or a combination of differentmaterials. It can be advantageous when the inlet slide is composed ofabout 20% lead and 80% PTFE, namely by volume. The above-mentionedportions for making a slide layer are given in percent by weight. It isadvisable for the slide layer to amount to at least 0.1 mm, whereby iscan be advisable when it has between 0.2 mm and 0.4 mm.

Those regions of a slide shoe that form a slide layer can be produced inone piece with the base body of the slide shoe, or else they can besprayed on, clipped on, or bonded.

In addition to or alternative to the described slide layer, a slidelayer can be provided in the regions 217 a (see FIG. 9) that surround anenergy storage device. The slide layer can be provided directly on theregions 217 a, or else it can be part of a wear protector 26 describedin connection with FIGS. 1 and 2. The fundamental substance of such awear protector can be composed of a sheet metal strip or a shaped sheetmetal part on which the slide layer is applied.

As also can be seen particularly in connection with FIG. 3, the supportshoes 27 have regions 48, 49 that project radially inwardly and are hereformed by nose- or hook-shaped regions 48, 49. Noses 48, 49 eachencompass the radially outer section 50 of a coil spring winding 8 a.The form lock thereby formed between the support shoes 27 and theassociated windings 8 a ensure at least a positioning or securing of thesupport shoes 27 or the support elements 25 in the longitudinaldirection of the spring 8.

Furthermore, through the special formation of the regions or noses 48,49, which are especially apparent from FIG. 3, a preferred force-lockingconnection between the support shoes 27 and the associated springwindings 8 a is also ensured in the radial direction. The thereby formedholding of the support shoes 27 on the associated windings 8 a in adirection perpendicular to the longitudinal axis 51 (FIG. 2) of theenergy storage device 7 (FIG. 2), makes possible in an advantageous waya preassembly of the support elements 25 on the corresponding spring 8.Thereby the assembly of a torsional vibration damper 1 is substantiallysimplified. In an advantageous way the coil spring 8 provided withsupport elements 25 are arranged in curved form, whereby their assemblyis simplified.

The energy storage devices 7 that are assembled in connection with thesupport elements 25 are, as already mentioned, preferably of elongatedform, and therefore have a large ratio of spring length/outer diameterwhich can be of the order of magnitude between 5 and 20.

The configuration and arrangement of the energy storage devices 7preferably results in such a way that they limit the relative rotationbetween the input part and the output part of the torsional vibrationdamper 1, which is here formed of both inertial masses 2, 3. For thatpurpose, the coil springs 8 are preferably here loaded as a block inthat the radially inner lying winding sections 52 form a block so thatthey are in direct contact with each other. By the curved arrangement ofa spring 8 it is furthermore ensured that in the region of the radiallyouter sections 50 of the spring windings of a coil spring 8 sufficientfree space is provided in the circumferential direction to minimizecrushing or damage to the holding regions 48, 49 of the support shoes27. The latter can be realized by a suitable selection of the springwire that forms a spring 8, the coil diameter, the inclination of atleast individual windings and the radius of curvature provided to thespring. It can also be suitable when the windings 8 a received on asupport shoe 27 have another form than the windings provided between thewindings 8 a. Thus, for example, those windings 8 a can extend radiallyoutwardly relative to the adjacent windings, which can be achieved by anoval-like arrangement of windings 8 a. The corresponding windings 8 acan also have a larger outer diameter than the adjacent windings.

The regions 48, 49 are shaped in such a way that they form sections 53,54 (FIG. 50) that engage the back of winding 8 a. The regions 48, 49 arearranged in such a way that they have a certain elasticity or resiliencyso that the support shoes 27 can be clipped onto associated winding 8 a.In accordance with the invention, a snap connection can be providedbetween a support shoe 27 and the associated winding 8 a, which ensuresa loss-secure mounting of the shoes 27 to the associated spring 8.

The region that cooperates with spring winding 8 a, that also includesthe safety regions 48, 49, is preferably designed in such a way that thewinding 8 a has a certain angular degree of freedom relative to thesupport shoe 27, so that the winding 8 a can be deformed when the springis compressed and relaxed, without which a pivoting or rotation forcewould thereby be exerted on the support shoe 27. Thereby it is ensuredthat the support element 25 is constantly maintained in its optimalalignment and thereby functions acceptably. The pivot angle necessarytherefor is mainly dependent upon the inclination angle of the springwindings. It can be appropriate when the possible pivot angle between asupport shoe 27 and a spring winding 8 a is in the order of 2 to 100.However, it can also be suitable for that angle to be larger.

The regions of a support shoe 27 that encompasses a winding 8 a arepreferably designed in such a way that they encompass the wire 55 (FIG.3) that forms the winding 8 a both relative to its cross section andwell as over its longitudinal extent.

As is particularly apparent from FIGS. 1 to 5, a support shoe 27 has onboth sides of region 56 (FIG. 5) that receives or supports a springwinding 8 a, an extension or shoulder 57 that extends in a longitudinaldirection of spring 8, and that as can be concluded from FIG. 1encompasses the spring windings in an advantageous way over apredetermined angle. The extensions 57 in the illustrated exemplaryembodiment in cross section are formed in such a way that they diminishwith increasing distance from the region 56. In the illustratedexemplary embodiment the extensions of shoulders 57 are wedge-shaped incross section. Through the special arrangement of extensions orshoulders 57 it is ensured that also at high rotational speeds thewindings adjacent to the regions 48, 49 do not rest on the support shoes27, so that friction of those windings on the support shoes canpractically be avoided during compression and relaxation of springs 8.The support elements 25 are formed and arranged over the length of aspring 8 in such a way that they make possible a blocking force withoutcontact in the circumferential direction. The spacing between twosupport elements 25 that follow each other is preferably dimensioned insuch a way that the existing sections of a spring 8 between two elements25 that follow each other are sufficiently stiff in the radial directionto prevent contact of the spring windings on the support guide surface26 a, at least within a large rotational speed region of the engine. Athigher rotational speeds (for example greater than 4000 U/min.) suchcontact can however possibly take place, whereby the thus occurringsupport forces between the corresponding windings of a spring 8 and theguide surface 26 a are reduced.

By the only partially illustrated torsional vibration damper in FIG. 9 acomponent 217 of the torsional vibration damper radially supports theenergy storage device 207 composed of a plurality of compression coilsprings 208, 209, 209 a, on a region that overlaps in both an axial aswell as in a circumferential direction through a plurality ofdifferently formed support elements 225, 225 a and 225 b, at least undercentrifugal action.

The support elements 225 that are provided at the end regions of theenergy storage device 207 are composed of a roller body arrangement, bymeans of which they are supported on the inner surface of the region 217a, either directly or indirectly. The support elements 225 can besimilarly formed, as described in connection with FIGS. 1 to 5 or FIGS.6 and 7. Basically, however, other roller body arrangements are alsopossible, which will be described below.

The support elements 225 a that are provided in the middle region of theenergy storage device 207 are formed as slide shoes in the illustratedexemplary embodiment and can therefore have a similar functionality asthose described in connection with the slide shoe in accordance withFIG. 8.

In the illustrated exemplary embodiment of FIG. 9 a further supportelement 225 is provided at a certain distance from the support elements225 at the end regions of the energy storage device 207, which likewisehas a roller body arrangement. It can thereby be ensured that a longerlength of the energy storage device 207 can be compresses and relaxedpractically without frictional hysteresis.

It is further understandable from FIG. 9 that a support element 225 b isprovided between the two support elements 225 that follow on behind theother at respective end regions of the energy storage device 207, thathas a radial spacing 260 relative to the inner support surface of theregion 217 a, at least when the torsional vibration damper is notrotating. In a suitable way, the support elements 225 b have a radialconnection with at least one winding so that it is also not disengagedfrom the spring 208 under the action of centrifugal force.

The distance between the two support elements 225 with roller bodyarrangements and that follow one another is dimensioned in anadvantageous way such that the regions of the energy storage device 207provided therebetween is sufficiently rigid in the radial direction toprevent the support of the corresponding spring regions of a contactbetween the corresponding support elements 225 b on the inner wall ofthe region 217 a, at least over a large rotational speed range of theengine. At higher rotational speeds such support or contact cannevertheless take place whereby on the basis of the support element 225b that functions as a slide shoe both the deflection of thecorresponding regions of the energy storage device 207 as well as thefriction that acts is limited. The roll shoes formed by the supportelements 225 and the at least one slide shoe 225 b arranged between twosuch roll shoes therefore make possible the realization of larger freeresilient partial lengthening of an energy storage device 207.

In the illustrated exemplary embodiment the above-described arrangementof roll shoes 255 and slide shoes 225 b is provided at both ends of theenergy storage device 207. One such arrangement can nevertheless also beprovided only at an end or else over the entire length. It isadvantageous if the above-described combination of roll shoes 225 andslide shoes 225 b are provided at least at the end region of an energystorage device 207, which during acceleration of the motor vehicleequipped with a corresponding torsional vibration damper is mainlyloaded or compressed.

The use of support elements in accordance with the invention, such as,for example, slide shoes or rolling shoes, that serve to radiallysupport a region of an energy storage device acted upon by centrifugalforce, and that ensure a support function for an energy storage deviceat higher rotational speeds, and take place in combination with anyregularly operating support elements, for example, 225 and/or 225 a.That principle can therefore also be utilized in a supporting guide forenergy storage devices, which have only slide shoes. In the embodimentillustrated in FIG. 9, only a corresponding arrangement of slide shoes225 a and 225 b can therefore be utilized.

For many applications it can also be appropriate, at least when thetorsional vibration damper is not rotating, for the support elements tobe loosely engaged, having radial play between the adjacent supportelements such as, for example, 225 in accordance with FIG. 9, and thushave no longitudinally effective connection with the energy storagedevice. In such an arrangement the support elements, such as, forexample, slide shoe 225 b, can be supported under the effect ofcentrifugal force on the inner surface of the surrounding region 217 aand regions of spring 208 of the energy storage device 207, first cometo rest on those support elements, such as, for example, slide shoes 225b at higher rotational speeds.

As already mentioned, the energy storage device 207 shown as anexemplary embodiment in FIG. 9 is composed of three coil springs 208,209, 209 a. In such an arrangement of the energy storage device an atleast two-stage characteristic curve can be achieved. By utilizing innercoil springs 209, 209 a having different spring stiffnesses, an at leastthree-stage characteristic curve can also be achieved, because when oneof both springs 209, 209 a with weaker spring characteristic becomesblocked the inner spring having a stronger spring characteristic stillhas residual spring travel. As is further apparent from FIG. 9, betweenthe associated end regions of inner springs 209, 209 a, at least inrelaxed condition of the energy storage device 207 a circumferentialspacing is provided. If needed, that spacing can be at least partiallyfilled by a further inner spring, so that then still further variationpossibilities are realizable relative to the overall characteristiccurve of the energy storage device 207.

By utilizing inner springs 209, 209 a with different springcharacteristics, it is appropriate to provide the spring with the lowerstiffness at the end or in the end region of the energy storage device207 that is mainly stressed during pulling operation of a motor vehicleequipped with a corresponding torsional vibration damper. The weakerinner spring should therefore be provided at the end region of theenergy storage device 207 which surrounds the end of energy storagedevice 207, through which the torque produced by the drive engine duringpulling operation is introduced into the energy storage device 207.During slowing operation the torque is introduced at the other end ofthe energy storage device 207. Slowing operation of a motor vehicle isthen provided when the vehicle is retarded by the braking operation ofthe engine, thus when a torque flow is produced by the drive wheels tothe engine.

The limit of spring travel of an energy storage device 207 can takeplace by contact of at least the radially inner winding regions of theouter spring 208, or else by the inner springs 209, 209 a that areconnected in series.

It can be advisable when the parallel-connected outer spring 208 and theinner spring with lower stiffness, for example, 209 a, has a resultingspring rate of the order of magnitude of between 5 and 13 Nm/°. Therotational stiffness of the outer coil spring 208 and that of the springoperating parallel thereto with higher stiffness, for example, 209 canbe of the order of magnitude of between 12 and 23 Nm/°.

In the exemplary embodiment illustrated in FIGS. 10 and 11, at leastsome of the energy storage devices 307, which can be partially formed bycoil springs, include centrifugally supported elements 335 formed byroller shoes. The roller shoes 335 have a base 327 on which the energystorage device is radially supported, as well as a roller bodyarrangement 328, which ensures the radial support between the base 335and a radially outer track that in the present case is formed by a wearprotector 326. The wear protector 326 is arranged similar to thatdescribed in connection with the wear protector 26 in accordance withFIGS. 1 and 2. In case the wear protector 326 is not needed, it can alsobe eliminated so that then a roller shoe 335 can be supported directlyon the axially surrounding regions 317 a about an energy storage device307 of a component 317 of the torsional vibration damper 301 that isformed as a two-mass flywheel.

As can be gathered from FIGS. 10 and 11, the roller body arrangement 328has two roller body rotation arrangements that have balls 330 in theillustrated embodiment. The balls 330 are received and guided in thebase 327 for which corresponding channels are provided in respectivebases 335 for the rotational transport or the continuous transport ofthe roller bodies 330. In the illustrated exemplary embodiment anintermediate wall 336 is provided that is preferably formed from ametallic insert. The intermediate wall 336 is supported radially by thebase 327 of a roller shoe 325.

As can be gathered from FIGS. 10 and 11, the balls 330 are foundradially outward of the intermediate wall 336 and are supported radiallyinwardly by intermediate wall 336 and radially outwardly by the rollingsurface on the wear protector 326, so that when a roller shoe 325 ismoved relative to the wear protector 326 the corresponding balls 330execute a rolling movement and are guided along the channels that areradially below the intermediate wall 336, so that the balls 330 can passalong the circular paths formed by the corresponding channels. Theroller body arrangements 329 and 329 a therefore have a radial ballrecirculation arrangement. It is further apparent from FIG. 10 that therecirculating ball arrangements 329, 329 a are formed in such a way thatthe directly further inner balls 330 of both arrangements 329, 329 a arespaced further from each other than the directly radially outer balls330. As also apparent from FIG. 10, the roller body arrangements 329,329 a are therefore arranged V-like, whereby the imaginary apex isdirected radially outwardly. The V-shaped arrangement can however alsobe designed inverted, so that then the imaginary apex points radiallyinwardly. For many applications it can also be suitable for the rollerbody recirculation arrangements 329, 329 a to be arranged in such a waythat the radially outwardly positioned balls and the radially furtherinner balls are practically directly radially arranged one above theother. The radially outwardly situated balls 330 on the intermediatewall 336 can be supported in a conventional way, such as by deep groovedball bearings, or else the support contours for the balls 330 formed bythe intermediate wall 336 can be designed in such a way that the ballsare supported by the intermediate wall 336 similar to an angular contactball bearing. The roller pathways of both roller body arrangements 329,329 a for the balls that are located further radially outwardly canthereby be provided similar to a two-row angular contact ball bearing.

Instead of balls 330 short needles or barrels can also be utilized asroller elements.

As already mentioned, the roller body arrangements 329, 329 a aredesigned in such a way to provide a practically radially oriented rollerbody path. In the embodiment shown in FIG. 12 both roller bodyarrangements 429, 429 a are designed in such a way to provide apractically axial roller body path.

In the exemplary embodiment illustrated in FIG. 12 the centrifugalsupport results from the axially outer ball rows 430 a, 430 b. For manyapplications it can however also be suitable for both middle ball rowsto serve as radial support and the axially further spaced ball races arefound in a circumferential channel.

The utilization of support elements with circulating roller bodyarrangements has the advantage that such support elements are notlimited relative to the permitted swing angle or rotation angle, andthereby, if necessary, such support elements can be installeddistributed over the full length of a long energy storage device.

In the embodiment in accordance with FIG. 13 a roller body ring 529 isutilized that can extend along the circumference of regions 517 a thatsupport the energy storage devices 507. The roller body ring 529 has atleast one, preferably two roller body circulation arrangements 530 a,530 b that extend along the full circumference of the internal surfacesof the regions 517 a. The support shoes 527 linked to the energy storagedevices 507 can roll along those roller body arrangements 530 a, 530 b.The roller body arrangements 530 a, 530 b are therefore not connectedwith the support shoes 527, but with the roller body ring 529 that isarranged between the regions 517 a and the shoes 527.

As can be gathered from FIGS. 14 and 15, a roller body ring 529 can alsohave a plurality of roller body arrangements 530 a, 530 b arranged overits length at smaller, angular extent. In the embodiment in accordancewith FIG. 14, the individual roller body arrangements 530 a, 530 b areoffset in the longitudinal direction, or circumferential direction ofthe ring 529, whereas in the embodiment in accordance with FIG. 15 nocircumferential offset is provided between roller body arrangements 530a, 530 b that are arranged in parallel with each other in thelongitudinal direction of the ring 529.

In the embodiment in accordance with FIG. 16, the support of an energystorage devices 607 is in places the result of retainer elements 627that at least in places overlap or encompass the energy storage device627 and are supported on components 617, 618 of a torsional vibrationdamper 601 formed as a two-mass flywheel by means of roller bodycirculation arrangements 630 a, 630 b.

The components 617, 618 in the illustrated exemplary embodiment aredesigned similar to the components 17, 18 described in connection withFIGS. 1 and 2.

The retaining elements 627 associated with an energy storage device orat least an elongated coil spring can be of shell-like form and, asshown, can be designed as sheet metal parts or else also of plastic orof a combination of several materials. The circumferential connectionbetween the at least one coil spring and the associated retainingelements 627 can result as described in connection with FIGS. 1 to 7,that is, by means of a form-lock. For many applications, however, simplya frictional connection can be sufficient.

In the embodiment in accordance with FIG. 17, the flange 716, which canbe concentrically securely connected by roller body circulation shoes750 with the transmission side inertial mass, is centered relative to,for example, the inertial mass 702 provided on the engine side. By sucha centering of the flange 716, which relative to its function iscomparable to the flange 16 in accordance with FIGS. 1 and 2, thecentering bearing 4 provided in FIGS. 1 and 2 can be eliminated.

As can be seen from FIG. 17, roller body circulation shoe 750 is formedsimilar to the roller body circulation shoes 725 that support the coilsprings 708.

As can be seen from FIG. 18, the inventive configurations andarrangements of support elements 827, 828 can be utilized with at leastone roller body circulation arrangement 730 a, 730 b, and in anespecially advantageous way in connection with elongated energy storagedevices 707 that are composed of short, individual energy storagedevices 708, 708 a, 708 b connected in series. As shown, the individualshorter energy storage devices can be composed of a single coil spring,or else also of several coil springs that are nested within each other,whereby the nested coil springs can have equal or different lengths. Ascan be seen from FIG. 18, the roller body circulation shoes 828 areformed in such a way that they have a radially inwardly extendingprojection 828 b, that here is wedge-shaped, that engages between theend windings of two adjacent, shorter energy storage devices. The rollerbody circulation shoes 828 have regions directed in the circumferentialdirection, which overlap the associated energy storage devices forradial support.

By one embodiment, at least in accordance with FIG. 16, the supportelements 627, which namely are associated with different energy storagedevices, can be non-rotatably connected to each other, however relativeto the compression path they support the same regions of the differentenergy storage devices. For that purpose the individual support elementscan be non-rotatably connected together, for example by an annularlocked region.

The slide shoe 825 shown in section in FIG. 19 and in a perspective viewin FIG. 20, can be coupled with a coil spring or an energy storagedevice in a manner similar to the connection with the roller or slideshoes described in accordance with FIGS. 1 to 5.

It can be seen in FIGS. 19 and 20 that a slide shoe 825 has radiallyouter formations 860, 860 a that here are formed as recesses or groovesthat are open radially outwardly. As is apparent especially from FIG.19, the formations 860, 860 a are wedge-shaped, whereby thosewedge-shaped grooves 860, 860 a extend outwardly from the center of theslide shoe 825. Between the outlet regions of the groove-like formations860, 860 a the slide shoe 825 has a slide surface region 861.

As is apparent especially from FIG. 20, the wedge-shaped recessformations 860, 860 a extend only partially over the entire width of aslide shoe 825, so that on both sides of the formations 860, 860 a thereremain guide sections 862, 863 directed in the circumferentialdirection. It is advisable to provide such guide sections 862 and/or 863at least over partial regions of the width of a slide shoe 825 toprevent tipping of the slide shoe 825 or a pivoting relative to theregion 861.

In the embodiment shown in FIG. 20 the width of the recessed formations860, 860 a is constant.

In the embodiment illustrated in FIG. 21, the formations 960, 960 a areformed as a taper or wedge shape from the middle region 961 of the slideshoe 925 outward.

By an appropriate determination of the wedge angle 862 a indicated inFIG. 19 as well as the width pattern of the formations 860, 860 a or960, 960 a, the buildup of a hydrodynamic lubricant film between slideshoe 825 or 925 and their radially supported guide surfaces can bepositively influenced. Thereby the friction or rotational resistance,especially by a displacement of a slide shoe 825 or 925 along its guidesurface can be substantially reduced.

In the illustrated exemplary embodiments of the slide shoes 825, 925starting from a circumferential end has only one formation 860, 960 or860 a, 960 a. However, it can also be suitable when at least two suchformations 860, 960 or 860 a, 960 a are provided over the width of aslide shoe 825, 925, that in each case have a correspondingly smallerwidth. By one such arrangement the formations starting from both endregions associated with a slide shoe 825 or 925 are aligned with eachother, therefore provided in alignment relative to the sliding movementdirection of a slide shoe 825. However, it can also be suitable when theformation 860 starting from one end in reference to the formation 860 astarting from the other end, viewed over the width of a slide shoe 825,are arranged offset to each other.

The arrangements and operating modes in accordance with the inventioncan be utilized with particular advantage in conjunction with so-calledtwin-mass flywheels, which are known, for example, through DE-OS 4 117582, DE-OS 4 214 655, DE-OS 4 414 584, DE-OS 4 420 927 and DE-OS19522718. Basically, however, the invention can also be utilized inconjunction with each of any torsional vibration dampers that have coilsprings, such as, for example, clutch discs or belt pulley dampers.

The arrangements and operating modes in accordance with the inventioncan also be installed in an advantageous way in lockup clutches withtorsional vibration dampers for hydrodynamic torque converters. Suchlockup clutches are known, for example, through the following patentsU.S. Pat. No. 5,868,228, U.S. Pat. No. 5,769,195, U.S. Pat. No.5,279,398 and U.S. Pat. No. 5,377,796.

In connection with the invention, energy storage devices that have alleast one coil spring can be installed in an advantageous way asproposed, for example, in DE-OS 4 229 416, DE-OS 4 406 826, DE-OS19603248, DE-OS 19648342, DE-OS 19909044 and DE-OS 19912970.

The patent claims submitted with the application are formulationproposals without prejudice for attaining more extensive patentprotection. The applicant reserves the right to claim additional featurecombinations previously disclosed only in the description and/ordrawings.

References utilized in the dependent claims refer to the furtherdevelopment of the object of the main claim through the features of therespective dependent claim. They are not to be understood as a waiver ofattaining an independent, objective protection for the featurecombinations of the referred-to dependent claims.

Since the objects of the dependent claims could, with respect to thecondition of the art on the priority day, form their own and independentinventions, the applicant reserves the right to make them the objects ofindependent claims or statements of division. They can furthermore alsocontain independent inventions, which have a configuration independentof the objects of the preceding dependent claims.

The exemplary embodiments are not to be understood as a restriction ofthe invention. Rather, numerous changes and modifications are possiblein the framework of the present disclosure, especially such variants,elements and combinations and/or materials which can, for example, bededuced by the specialist with regard to the solution of the object bythe combination or modification of individual features or elements orprocedural steps in connection with the general description andembodiments as well as described in the claims or contained in thedrawings, and which lead by combinable features to a new object or tonew procedural steps or procedural step sequences, also to the extentthat they concern manufacturing, testing and operating procedures.

1. A torsional vibration damper comprising: at least two parts rotatablerotatably movable relative to each other about an axis of rotation inopposition to the operation of at least one energy storage device,whereby both parts have regions by means of which the energy storagedevice is disposed in a circumferential direction of the torsionalvibration damper and is compressible, at least one of the parts that arerelatively rotatable has a wall region that axially overlaps at leastradially outer regions of the energy storage device and extends alongthe energy storage device, wherein the energy storage device is radiallyoutwardly supported by at least one support element that is arrangedbetween the energy storage device and the wall region and is movablealong the wall region upon compression of the energy storage device,whereby the support element has at least one support shoe engaging atleast one region of the energy storage device, and at least one rollerbody is provided between the support shoe and the wall region forrolling movement along a surface carried by the support shoe.
 2. Atorsional vibration damper in accordance with claim 1, wherein theroller body can execute a rolling movement at least relative to sectionsof the said wall region.
 3. A torsional vibration damper in accordancewith claim 1, wherein the at least one roller body rolls directly onsections of the wall region.
 4. A torsional vibration damper inaccordance with claim 1, including an intermediate element providedbetween the wall region and the at least one roller body, wherein theintermediate element is movable along the wall region and forms asupport surface for the at least one roller body.
 5. A torsionalvibration damper in accordance with claim 4, wherein the intermediateelement has limited movability relative to the support shoe and during amovement the at least one roller body is supported on a surface of thesupport shoe and on a surface of the intermediate element.
 6. Atorsional vibration damper in accordance with claim 1, wherein aplurality of roller bodies are provided arranged one after another inthe circumferential direction of the torsional vibration damper.
 7. Atorsional vibration damper in accordance with claim 1, wherein theroller bodies are formed as balls, rollers or needle rollers.
 8. Atorsional vibration damper in accordance with claim 6, wherein theroller bodies are positioned one after another in a cage.
 9. A torsionalvibration damper in accordance with claim 1, wherein the at least oneroller body can execute only a limited movement relative to the supportshoe.
 10. A torsional vibration damper in accordance with claim 4,wherein the intermediate element is slidable along the wall region. 11.A torsional vibration damper in accordance with claim 4, wherein atleast one of the support shoe and the intermediate element is composedof plastic.
 12. A torsional vibration damper in accordance with claim11, wherein at least one of the support shoe and the intermediateelement has a metallic insert that forms a roller path for the at leastone roller body.
 13. A torsional vibration damper in accordance withclaim 1, wherein the torsional vibration damper has at least two energystorage devices that extend over at least 90° in the circumferentialdirection of the torsional vibration damper, and at least adjacent endregions of the energy storage devices are radially supported by asupport element.
 14. A torsional vibration damper in accordance withclaim 13, wherein regions of the energy storage devices that lie betweenthe end regions are supported by a support element.
 15. A torsionalvibration damper in accordance with claim 13, wherein at least thesupport elements provided in the end regions of an energy storage deviceinclude roller bodies.
 16. A torsional vibration damper in accordancewith claim 1, wherein the energy storage device is formed from at leastone coil spring.
 17. A torsional vibration damper in accordance withclaim 16, wherein the at least one coil spring is guided in acurvilinearly extending retainer that is formed from regions of at leastone of both parts that are rotatably movable relative to each other,whereby the retainer is bounded by the wall regions and the support shoeradially supports at least one winding of the spring.
 18. A torsionalvibration damper in accordance with claim 17, wherein the support shoehas at least one region that at least partially surrounds a radiallyouter section of a coil spring, whereby the support shoe is fixedrelative to the coil spring in the longitudinal direction of the coilspring.
 19. A torsional vibration damper in accordance with claim 17,wherein a connection is provided between the support shoe and the coilspring, which connection produces a holding of the support shoe relativeto the coil spring in a direction perpendicular to the longitudinal axisof the coil spring.
 20. A torsional vibration damper in accordance withclaim 19, wherein the holding of the support shoe on the coil springtakes place through the region of the support shoe that at leastpartially surrounds one winding of the coil spring, whereby the regionthat at least partially surrounds a wire that forms the winding producesat least one of a force-locking and a form-locking connection with thewinding.
 21. A torsional vibration damper in accordance with claim 19,wherein the holding of the support shoe takes place on a spring windingby a snap-on connection.
 22. A torsional vibration damper in accordancewith claim 20, wherein the holding provided between the support shoe andthe corresponding spring winding allows at least a small angularrotational movement of the winding relative to the support shoe.
 23. Atorsional vibration damper in accordance with claim 22, wherein therotational movement lies in the order of magnitude of from 2° to 10°.24. A torsional vibration damper in accordance with claim 1, wherein thedamper includes a divided flywheel whereby a primary flywheel isconnected with a drive shaft of an engine and a secondary flywheel isconnected with an input shaft of a transmission, and wherein regions ofat least one of the flywheels bound an annular chamber in which at leasttwo circumferentially arranged energy storage devices are received.